JP6611997B2 - Heat exchange unit and air conditioner equipped with the same - Google Patents

Description

  The present invention relates to a heat exchange unit and an air conditioner equipped with the heat exchange unit.

  For example, in Patent Document 1, a casing in which an inlet and an outlet are formed, a bell mouth disposed in the casing, a centrifugal fan installed behind the bell mouth, and a centrifugal fan are surrounded. An air conditioner including an installed heat exchanger is disclosed. In the air conditioner described in Patent Document 1, the air sucked from the suction port is blown out from the outlet through the bell mouth, the centrifugal fan, and the heat exchanger.

JP 2000-356362 A

  When the heat exchanger is arranged so as to surround the periphery of the centrifugal fan as in the air conditioner described in Patent Document 1, the heat exchanger is located on the surface far from the blowout port, that is, on the center side of the housing. Air hardly flows, and the efficiency of the heat exchanger is greatly reduced. For this reason, the efficiency of a heat exchanger is greatly influenced by the installation position of a blower outlet, As a result, restrictions are imposed on the installation positions of a suction inlet and a blower outlet. Therefore, the housing | casing with which the air conditioner of patent document 1 is provided is a thing with a small installation freedom according to the form of an actual building and floor plan. Most of the conventional air conditioner casings have the same configuration as that of the air conditioner casing described in Patent Document 1.

The present invention has been made against the background of the problems described above, an air conditioning apparatus equipped with the heat exchange unit and the heat exchange unit to pass issued release from centrifugal fan wind efficiently heat exchanger It is intended to provide.

The heat exchange unit according to the present invention is formed with an intake air passage communicating with the air inlet and a blow air passage communicating with the air outlet, and has the smallest dimension in the height direction among the height, width, and depth dimensions. A body, a first partition plate that vertically divides the inside of the housing into the intake air passage and the blowout air passage, and a bell mouth installed at a periphery of an opening formed in the first partition plate If the installed in the first partition plate through the bell mouth, and a centrifugal fan which is adapted to be blown air in a circumferential direction in the outlet air passage, downstream of the centrifugal fan or an internal of the casing A heat exchanger disposed on a side of the centrifugal fan. A side surface, a second side surface, and the air outlet is open to the front surface The intake port is formed in the rear surface, and the intake air passage is formed on the rear surface between a fan intake port that is an intake port of the centrifugal fan and the main plate closest to the fan intake port. The heat exchanger has upper and lower heat exchangers on the front side of the centrifugal fan, and the lower heat exchanger has the outlet on the upper side and the centrifugal fan. The upper heat exchanger is disposed so as to be inclined so that the blower outlet side is down and the centrifugal fan side is up, and separates the intake air passage and the blowout air passage The intake air blow-off partition plate prevents the intake air passage from reaching the front surface of the housing, and the heat exchanger is disposed closer to the air outlet than the suction blow-off partition plate .

According to the heat exchange unit of the present invention, the intake port can be formed on any surface of the casing forming the intake air passage, and any of the casings forming the blowout air path can be formed. Since the air outlet can be formed on the side surface, the degree of freedom in installation can be improved. In addition, by forming the intake air passage from the suction port of the centrifugal fan to the rear surface along the main plate closest to the suction port of the centrifugal fan, a wide space between the centrifugal fan and the rear surface of the housing should be secured. Can do. Therefore, the wind blown to the rear surface side (surface far from the blower outlet) of the centrifugal fan can be efficiently passed through the heat exchanger.
In addition, according to another heat exchange unit of the present invention, the centrifugal fan that blows air in the circumferential direction in the blowing air passage, and the upper and lower heat exchangers on the front side of the centrifugal fan are provided. The lower heat exchanger is inclined so that the outlet side is up and the centrifugal fan side is down, and the upper heat exchanger is inclined so that the outlet side is down and the centrifugal fan side is up The wind discharged from the centrifugal fan can be efficiently passed through the heat exchanger.

It is a schematic top view which shows roughly the state which looked at the heat source machine which is one of the heat exchange units which concerns on Embodiment 1 of this invention from the upper surface. It is a schematic sectional drawing which shows roughly an example of the AA cross section of FIG. It is a schematic sectional drawing which shows schematically another example of the AA cross section of FIG. It is a schematic sectional drawing which shows schematically another example of the AA cross section of FIG. FIG. 3 is a graph showing an example of a relationship between a ratio of intake port height and housing height and ventilation resistance in the heat exchange unit shown in FIG. 2. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 1 of this invention from the upper surface. It is a schematic top view which shows schematically the state which looked at the other example of the heat source machine which is one of the heat exchange units which concern on Embodiment 1 of this invention from the upper surface. It is a schematic top view which shows roughly the state which looked at the other example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 1 of this invention from the upper surface. It is the schematic which showed an example of the heat exchanger mounted in the heat source machine which is one of the heat exchange units which concerns on Embodiment 1 of this invention. It is the schematic which showed another example of the heat exchanger mounted in the heat source machine which is one of the heat exchange units which concerns on Embodiment 1 of this invention. It is a graph which shows an example of the wind speed distribution of the centrifugal fan at the time of mounting the heat exchanger shown in FIG. It is a perspective view which shows roughly a part of heat exchanger using a circular pipe as a heat exchanger tube. It is a perspective view which shows roughly a part of heat exchanger using a flat tube as a heat exchanger tube. It is the schematic which shows roughly an example of a structure of the heat exchanger using a corrugated fin. It is a schematic sectional drawing which shows an example of a heat exchanger corresponding to the AA cross section of FIG. It is a schematic sectional drawing which shows roughly another example of a heat exchanger corresponding to the AA cross section of FIG. It is a schematic sectional drawing which shows roughly another example of a heat exchanger corresponding to the AA cross section of FIG. It is a schematic top view which shows schematically the state which looked at the heat source machine which is one of the heat exchange units which concerns on Embodiment 2 of this invention from the upper surface. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 2 of this invention from the upper surface. It is a schematic top view which shows roughly the state which looked at the other example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 2 of this invention from the upper surface. It is an outline top view showing roughly the state where another example of the heat source machine which is one of the heat exchange units concerning Embodiment 2 of the present invention was seen from the upper surface. It is an outline top view showing roughly the state where another example of the heat source machine which is one of the heat exchange units concerning Embodiment 2 of the present invention was seen from the upper surface. It is a schematic sectional drawing which shows roughly an example of the AA cross section of FIG. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 2 of this invention from the upper surface. It is a schematic top view which shows roughly the state which looked at the other example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 2 of this invention from the upper surface. It is an outline top view showing roughly the state where another example of the heat source machine which is one of the heat exchange units concerning Embodiment 2 of the present invention was seen from the upper surface. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 3 of this invention from the upper surface. It is a schematic top view which shows the state which looked at the other example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 3 of this invention from the upper surface. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 4 of this invention from the upper surface. It is a schematic sectional drawing which shows roughly an example of the AA cross section of FIG. It is a graph which shows an example of the analysis result at the time of providing a bypass wind path. It is a schematic top view which shows schematically the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 4 of this invention from the upper surface. It is a schematic sectional drawing which shows roughly an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 5 of this invention corresponding to the AA cross section of FIG. It is a schematic top view which shows roughly the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 6 of this invention from the upper surface. It is a schematic sectional drawing which shows roughly an example of the AA cross section of FIG. It is the schematic which shows roughly the state which looked at the example of the heat exchanger by the cross section side. It is the schematic which shows roughly the state which looked at the example of the heat exchanger by the cross section side. It is the schematic which shows roughly the state which looked at the cross section of another example of arrangement | positioning of a heat exchanger. It is a schematic top view which shows roughly the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 7 of this invention from the upper surface. It is a schematic top view which shows roughly the state which looked at an example of the heat source machine which is one of the heat exchange units which concerns on Embodiment 8 of this invention from the upper surface. It is a schematic sectional drawing which shows roughly an example of the AA cross section of FIG. In the heat exchange unit which concerns on Embodiment 8 of this invention, it is a figure for demonstrating the relationship between the position of a centrifugal fan, and ventilation resistance. In the heat exchange unit which concerns on Embodiment 8 of this invention, it is a graph which shows an example of the relationship between the distance from the rotation center axis | shaft of a centrifugal fan to a rear surface, the ratio of a fan radius, and ventilation resistance. It is a graph which shows an example of the relationship between the inclination-angle of a heat exchanger, and ventilation resistance in the heat exchange unit which concerns on Embodiment 8 of this invention. It is the figure which showed roughly another example of the heat exchanger which concerns on Embodiment 8 of this invention corresponding to the AA cross section of FIG. It is the figure which showed roughly another example of the heat exchanger which concerns on Embodiment 8 of this invention corresponding to the AA cross section of FIG. It is a schematic top view which shows roughly the state which looked at the example of the load side machine which is one of the heat exchange units which concerns on Embodiment 9 of this invention from the upper surface. It is a block diagram which shows roughly an example of the refrigerant circuit structure of the air conditioning apparatus which concerns on Embodiment 10 of this invention. It is a block diagram which shows roughly an example of the refrigerant circuit structure of the air conditioning apparatus which concerns on Embodiment 10 of this invention. It is a block diagram which shows roughly an example of the refrigerant circuit structure of the modification of the air conditioning apparatus which concerns on Embodiment 10 of this invention.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Further, in the following drawings including FIG. 1, the same reference numerals denote the same or equivalent parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
FIG. 1 is a schematic top view schematically showing a state in which the heat source unit 1a-1 that is one of the heat exchange units according to Embodiment 1 of the present invention is viewed from above. FIG. 2 is a schematic cross-sectional view schematically showing an example of the AA cross section of FIG. FIG. 3 is a schematic cross-sectional view schematically showing another example of the AA cross section of FIG. 1. FIG. 4 is a schematic cross-sectional view schematically showing still another example of the AA cross section of FIG. 1. Hereinafter, the heat source unit 1a-1 will be described with reference to FIGS. In addition, in FIG. 1, the inside of heat-source equipment 1a-1 is shown typically. Moreover, in FIGS. 2-4, the flow of air is represented by arrow A1 and arrow A2. Furthermore, in FIG. 1 to FIG. 4, a state in which the right side of the paper is the rear surface of the heat source device 1 a-1 and the left side of the paper surface is the front of the heat source device 1 a-1 is shown as an example.

The heat source machine 1a-1 according to the first embodiment constitutes a part of the air conditioner together with the load side machine. The air conditioner is used, for example, for heating or cooling a room such as a house, a building, or a condominium, that is, an air-conditioning target space. The air conditioner has a refrigerant circuit in which element devices mounted on the load side unit and the heat source unit 1a-1 are connected by piping, and heats or cools the air-conditioning target space by circulating the refrigerant through the refrigerant circuit. To do.
The air conditioner will be described in Embodiment 10.

The heat source machine 1a-1 is one of heat exchange units including a heat exchanger, and is used as an outdoor unit or a heat source unit.
A load side machine is also one of the heat exchange units provided with the heat exchanger, and is used as a load side unit, a use side unit, or an indoor unit.
The load side unit will be described in Embodiment 9.

  As shown in FIGS. 1 and 2, the heat source machine 1a-1 includes at least one heat exchanger 4, a compressor 1, a control box 2, a centrifugal fan 3, a bell mouth 40, a fan motor 13, And a drain pan 8. The heat exchanger 4, the compressor 1, the control box 2, the centrifugal fan 3, the bell mouth 40, the fan motor 13, and the drain pan 8 are installed in a housing 5 that constitutes the outline of the heat source unit 1 a-1. Here, the upper and lower surfaces of the centrifugal fan in the rotation axis direction are defined as the main plate, and the rotation direction of the centrifugal fan is defined as the side surface.

  The housing 5 has an air inlet 7 and an air outlet 10. The air inlet 7 and the air outlet 10 are formed so as to communicate the outside and the inside of the housing 5. For example, the air inlet 7 has an opening formed on one of the front surface, rear surface, side surface, and lower surface of the housing 5. The blower outlet 10 is formed with an opening in the front surface of the housing 5, for example. That is, the heat source unit 1a-1 does not take in air from the lower surface or the upper surface of the housing 5 or blow out air, but takes in air from one side of the housing 5 and draws air from the front of the housing 5. It comes to blow out.

The heat exchanger 4 is provided between the downstream side of the centrifugal fan 3 and the outlet 10.
The centrifugal fan 3 conveys air by rotating around an axis. The centrifugal fan 3 is installed on the partition plate 41 via the bell mouth 40. The centrifugal fan 3 is rotationally driven by a fan motor 13.
The bell mouth 40 is installed on the suction side of the centrifugal fan 3 and guides the air flowing through the intake air passage 14 </ b> A to the centrifugal fan 3. The bell mouth 40 has a portion where the mouth gradually narrows from the inlet on the intake air passage 14 </ b> A side toward the centrifugal fan 3.
The drain pan 8 is provided below the heat exchanger 4.

Further, an intake air passage 14 </ b> A and a blowout air passage 14 </ b> B partitioned by a partition plate 41 are formed inside the housing 5. In other words, the partition plate 41 that partitions the casing 5 up and down is provided in the casing 5, and the intake air passage 14 </ b> A and the blowout air passage 14 </ b> B are partitioned. The partition plate 41 is formed with an opening that allows the intake air passage 14A and the centrifugal fan 3 to communicate with each other, and a bell mouth 40 is installed at the periphery of the opening. Note that partitioning the housing 5 up and down means partitioning the housing 5 up and down in the state shown in FIG.
The partition plate 41 corresponds to a “first partition plate”.

The intake air passage 14 </ b> A communicates with the outside of the housing 5 through the intake port 7, and is a space through which the air passing through the intake port 7 always passes before being sucked into the centrifugal fan 3. As shown in FIG. 2, the intake air passage 14 </ b> A is formed in the lower part of the inside of the housing 5, and guides air taken in from the intake port 7 to the bell mouth 40 by communicating with the intake port 7.
The blowout air passage 14 </ b> B communicates with the outside of the housing 5 through the air outlet 10, and is a space through which air that has passed through the centrifugal fan 3 always passes. The blowout air passage 14 </ b> B is formed in the upper part of the inside of the housing 5, and communicates with the blowout port 10 to guide the air blown out from the centrifugal fan 3 to the blowout port 10.

  By providing the partition plate 41, the housing 5 has a two-story structure. By doing so, the direction of the intake port 7 can be changed by only attaching and detaching a part of the intake air passage 14A. That is, in the heat source unit 1a-1, the direction of the air inlet 7 can be selected from the front side, the side surface located on the paper surface in FIG. 1, the rear surface, and the side surface located below the paper surface in FIG. It has become. Therefore, according to the heat source device 1a-1, the direction of the air inlet 7 can be changed according to the installation location, and the degree of freedom in installation becomes high. Specifically, by removing a part of the side surface of the housing 5, the air inlet 7 can be attached to any of the front surface, the side surface located on the paper surface in FIG. 1, the rear surface, and the side surface located below the paper surface in FIG. 1. Can be formed.

  Note that a part of the intake air passage 14A includes, for example, a sheet metal that forms a bottom surface of the intake air passage 14A, a sheet metal that forms a side surface of the intake air passage 14A, and a fastening member such as a screw that fixes the sheet metal. It is. Further, the blower outlet 10 is also formed on the front surface, the side surface located on the paper surface of FIG. 1, the rear surface, and the side surface located below the paper surface of FIG. can do.

  In the housing 5 shown in FIG. 2, an air inlet 7 is formed on the rear surface of the housing 5, and an air outlet 10 is formed on the front surface of the housing 5. In this case, as shown by arrows A1 and A2 in FIG. 2, the air is taken in from the rear surface of the housing 5 and sucked from the lower part of the centrifugal fan 3 via the bell mouth 40, and the circumferential direction of the centrifugal fan 3 And heated or cooled by the heat exchanger 4 and blown out from the front of the housing 5.

  In the housing 5 shown in FIG. 3, an air inlet 7 is formed on the front surface of the housing 5, and an air outlet 10 is formed on the front surface of the housing 5. In this case, as shown by arrows A1 and A2 in FIG. 3, the air is taken in from the front of the housing 5 and sucked from the lower part of the centrifugal fan 3 via the bell mouth 40, and the circumferential direction of the centrifugal fan 3 And heated or cooled by the heat exchanger 4 and blown out from the front of the housing 5.

  In the housing 5 shown in FIG. 4, an air inlet 7 is formed on the lower surface of the housing 5, and an air outlet 10 is formed on the front surface of the housing 5. In this case, as shown by arrows A1 and A2 in FIG. 4, the air is taken in from the lower surface of the housing 5 and sucked from the lower part of the centrifugal fan 3 via the bell mouth 40, and the circumferential direction of the centrifugal fan 3 And heated or cooled by the heat exchanger 4 and blown out from the front of the housing 5. By providing the air inlet 7 on the lower surface of the housing 5, the opening area of the air inlet 7 can be increased, and the air path resistance at the air inlet 7 is reduced.

  Here, paying attention to the configuration shown in FIG. 2, the intake air passage 14 </ b> A faces one main plate of the housing 5 through the bell mouth 40 from the fan inlet 45 which is the inlet of the centrifugal fan 3, It is formed so as to reach the rear surface. With such a configuration, a wide space is secured for the blowout air passage 14B of the centrifugal fan 3. As shown in FIG. 2, when the height of the housing 5 is H1, and the height of the air inlet 7 is H2, the air inlet height H2 of the air intake passage 14A relative to the housing height H1 is the air flow of the heat exchange unit. The road resistance is greatly affected.

  FIG. 5 shows an example of an analysis result of an experiment conducted by the inventors. FIG. 5 is a graph showing an example of the relationship between the ratio of the inlet height and the casing height and the ventilation resistance in the heat exchange unit shown in FIG. The horizontal axis of FIG. 5 is the ratio value (H2 / H1) between the inlet height H2 and the casing height H1, and the vertical axis of FIG. 5 is the ventilation resistance. FIG. 5 shows the relationship between the ratio value (H2 / H1) and the ventilation resistance in an experiment in which the inlet height H2 is a constant value and the casing height H1 is changed within a range of 500 mm or less. Ventilation resistance decreases rapidly in the region where the ratio value (H2 / H1) is about 0.45 or less. Therefore, in the configuration in which the casing height H1 is 500 mm or less, the intake port height H2 of the intake air passage 14A is set in a range in which the ratio value (H2 / H1) is 0.45 or less. Air becomes easy to flow efficiently with respect to height. As a result, air circulation efficiency is improved.

2 to 4, the case where the air inlet 7 is formed on one surface of the housing 5 has been described as an example. However, the present invention is not limited to this configuration. It may be formed on the surface. In this way, the wind path resistance becomes smaller.
Further, the opening area of the air inlet 7 is not particularly limited, and a part of the rear surface of the housing 5 may be opened as the air inlet 7, or the entire rear surface of the housing 5 may be opened as the air inlet 7. Also good. Further, the number of intake ports 7 is not particularly limited.

  Here, the case where the flow of air is seen from the upper surface will be described. FIG. 6 is a schematic top view schematically showing a state of an example of the heat source device 1a-1 as viewed from above. FIG. 7 is a schematic top view schematically showing a state when another example of the heat source device 1a-1 is viewed from above. FIG. 8 is a schematic top view schematically illustrating a state of still another example of the heat source device 1a-1 as viewed from above. In addition, in FIGS. 6-8, the inside of heat-source equipment 1a-1 is shown typically. Moreover, in FIGS. 6-8, the flow of air is represented by arrow A3 and arrow A4. Further, in FIGS. 6 to 8, the right side of the paper is the rear surface of the heat source machine 1 a-1, the left side of the paper is the front surface of the heat source machine 1 a-1, and the upper side of the paper is the first side surface of the heat source machine 1 a-1. Is shown as an example in a state where the second side surface of the heat source unit 1a-1.

  In the housing 5 shown in FIG. 6, the air inlet 7 is formed on the second side surface of the housing 5, and the air outlet 10 is formed on the front surface of the housing 5. In this case, as indicated by an arrow A3 in FIG. 6, air is taken in from the second side surface of the housing 5, passes through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4, and then from the front of the housing 5. Blown out.

  In the housing 5 shown in FIG. 7, the air inlet 7 is formed on the rear surface of the housing 5, and the air outlet 10 is formed on the front surface of the housing 5. In this case, as indicated by an arrow A3 in FIG. 7, air is taken in from the rear surface of the housing 5 and is blown out from the front of the housing 5 after passing through the bell mouth 40, the centrifugal fan 3 and the heat exchanger 4. The

  In the housing 5 shown in FIG. 8, the air inlet 7 is formed on the first side surface of the housing 5, and the air outlet 10 is formed on the front surface of the housing 5. In this case, as indicated by an arrow A3 in FIG. 8, air is taken in from the first side surface of the housing 5, passes through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4, and then from the front of the housing 5. Blown out.

  In addition, although the inlet port 7 and the blower outlet 10 may be used by an open system, you may connect a duct etc. Moreover, the heat source machine 1a-1 may be any of a floor type, a ceiling type, or a ceiling embedded type. In the case of the ceiling-embedded type, the fan efficiency is high by using the centrifugal fan 3, and the casing 5 can be thinned. Note that the open system means that the air inlet 7 and the air outlet 10 are open to the outer space of each housing 5 without a duct or the like.

Next, the heat exchanger 4 will be described.
FIG. 9 is a schematic diagram illustrating an example of the heat exchanger 4 mounted on the heat source device 1a-1. FIG. 10 is a schematic diagram illustrating another example of the heat exchanger 4 mounted on the heat source device 1a-1. FIG. 11 is a graph showing an example of the wind speed distribution of the centrifugal fan 3 when the heat exchanger 4 shown in FIG. 10 is mounted. In addition, the arrow shown in FIG.9 and FIG.10 has shown an example of the refrigerant | coolant flow when the heat exchanger 4 is used as an evaporator, for example. In FIG. 11, the vertical axis indicates the heat exchanger height, and the horizontal axis indicates the wind speed.

As shown in FIGS. 9 and 10, the heat exchanger 4 includes a plurality of heat transfer tubes 15, a plurality of fins 18, a refrigerant distribution pipe 19, and a refrigerant collecting pipe 20.
The plurality of heat transfer tubes 15 are juxtaposed with each other and inserted through the plurality of fins 18. The heat transfer tube 15 can be formed of a circular tube or a flat tube.
The plurality of fins 18 are juxtaposed with each other at a constant pitch, and the plurality of fins 18 are inserted.
The refrigerant distribution pipe 19 is connected to each of the plurality of heat transfer tubes 15 and distributes the refrigerant to each of the heat transfer tubes 15.
The refrigerant collecting pipe 20 is connected to each of the plurality of heat transfer pipes 15 and merges the refrigerant that has flowed through the respective heat transfer pipes 15.

  The refrigerant decompressed by the decompression device, which is one of the component devices of the refrigerant circuit, flows into the refrigerant distribution pipe 19 and is distributed to each of the plurality of heat transfer tubes 15 by the refrigerant distribution pipe 19. The refrigerant flowing through each of the plurality of heat transfer tubes 15 exchanges heat with air at the fin connection portion, and then flows into the refrigerant collecting tube 20. In the refrigerant collecting pipe 20, the introduced refrigerant merges and flows out from the outlet of the refrigerant collecting pipe 20. The refrigerant that has flowed out of the refrigerant collecting pipe 20 is sucked into the compressor 1 that is one of the component devices of the refrigerant circuit. The refrigerant sucked into the compressor 1 is compressed and discharged. The refrigerant discharged from the compressor 1 flows into a condenser, which is one of the component devices of the refrigerant circuit, is subjected to heat exchange, and then decompressed by a decompression device. In this way, the refrigerant circulates through the refrigerant circuit.

  Although FIG. 9 shows the case where the heat transfer tubes 15 are juxtaposed in the horizontal direction, the present invention is not limited to this. For example, as shown in FIG. 10, the heat transfer tubes 15 may be arranged side by side in the vertical direction. In the case of the heat exchanger 4 shown in FIG. 10, the influence of the wind speed distribution of the centrifugal fan 3 in the height direction of the heat exchanger 4 can be reduced, and the heat exchange efficiency can be improved. That is, as shown in FIG. 11, the deviation of the wind speed can be reduced even in the height direction of the heat exchanger 4, and the heat exchange efficiency can be improved accordingly.

Next, the heat transfer tube 15 will be described.
FIG. 12 is a perspective view schematically showing a part of the heat exchanger 4 using the circular pipe 16 as the heat transfer pipe 15. FIG. 13 is a perspective view schematically showing a part of the heat exchanger 4 using a flat tube 17 as the heat transfer tube 15.

  In the heat exchanger 4 shown in FIG. 12, a circular tube 16 is used as the heat transfer tube 15. In this case, for example, as shown in FIG. 12, the circular tubes 16 may be arranged in a staggered manner. However, the circular tubes 16 may be arranged in one row, or the circular tubes 16 may be arranged in three or more rows.

  In the heat exchanger 4 shown in FIG. 13, a flat tube 17 is used as the heat transfer tube 15. In this case, for example, as shown in FIG. 13, the flat tubes 17 may be arranged in a staggered manner. However, the flat tubes 17 may be arranged in one row, or the flat tubes 17 may be arranged in three or more rows. The flat tube 17 has a larger heat transfer area than the circular tube 16 in the same volume. Therefore, according to the heat exchanger 4 using the flat tube 17, it can be mounted on a thin heat source machine or indoor unit with severe dimensional constraints, and the heat exchange efficiency can be further improved.

Next, a modified example of the heat exchanger 4 will be described.
FIG. 14 is a schematic view schematically showing an example of the configuration of the heat exchanger 4 using the corrugated fins 21. FIG. 15 is a schematic cross-sectional view schematically showing an example of the heat exchanger 4 corresponding to the AA cross section of FIG. FIG. 16 is a schematic cross-sectional view schematically showing another example of the heat exchanger 4 corresponding to the AA cross section of FIG. 1. FIG. 17 is a schematic cross-sectional view schematically showing still another example of the heat exchanger 4 corresponding to the AA cross section of FIG.

  9 and 10 show the heat exchanger 4 using the plate-like fins 18 as an example, but FIG. 14 shows the heat exchanger 4 using the corrugated corrugated fins 21 as an example. According to the heat exchanger 4 using the corrugated fins 21, high heat transfer performance can be obtained at low cost, and it can be mounted on a thin heat source unit or indoor unit with severe height dimension restrictions. Exchange efficiency can be improved.

  Although FIGS. 2-4 showed the case where the heat exchanger 4 was vertically arrange | positioned inside the housing | casing 5 as an example, it is not limited to this. For example, as shown in FIG. 15, the heat exchangers 4 configured by two heat exchange units may be arranged at different inclination angles. In FIG. 15, the lower heat exchanging part is inclined so that the blower outlet 10 side is up and the centrifugal fan 3 side is down, and the upper heat exchange part is so that the blower outlet 10 side is down and the centrifugal fan 3 side is up. The case where it is made to incline and arrange | positioned in the V shape of cross-sectional view sideways is shown in figure.

  By arranging the heat exchanger 4 as shown in FIG. 15, the heat exchanger can be mounted at a high density within the limited height restriction inside the housing 5. Therefore, the heat exchange efficiency can be improved by adopting the arrangement as shown in FIG. Further, by arranging as shown in FIG. 15, the distance between the blade tip of the centrifugal fan 3 and the heat exchanger 4 can be increased while mounting the heat exchanger at high density, that is, the distance can be increased. The effect of suppressing the generation of abnormal noise and noise can also be expected.

In addition, as shown in FIG. 16, one heat exchanger 4 may be disposed in an inclined manner. In FIG. 16, the case where the heat exchanger 4 is inclined and arranged so that the air outlet 10 side is on the upper side and the centrifugal fan 3 side is on the lower side is illustrated.
As shown in FIG. 16, by arranging the heat exchanger 4 in an inclined manner, the heat exchanger can be mounted at a high density within a limited height restriction inside the housing 5. Therefore, the heat exchange efficiency can be improved by adopting the arrangement as shown in FIG.

Moreover, as shown in FIG. 17, you may arrange | position the one heat exchanger 4 inclining. FIG. 17 illustrates a case where the heat exchanger 4 is inclined so that the air outlet 10 side is on the lower side and the centrifugal fan 3 side is on the upper side.
As shown in FIG. 17, by arranging the heat exchanger 4 in an inclined manner, the heat exchanger can be mounted at a high density within a limited height restriction inside the housing 5. Therefore, the heat exchange efficiency can be improved by adopting the arrangement as shown in FIG.

As shown in FIGS. 16 and 17, the inclination angle and inclination of the heat exchanger 4 so that the distance between the blade tip of the centrifugal fan 3 and the heat exchanger 4 can be increased according to the height position of the centrifugal fan 3. Select the orientation.
The case where the heat exchanger 4 is arranged vertically means that the air passage surface of the heat exchanger 4 is arranged so as to extend in the orthogonal direction with respect to the partition plate 41.
Furthermore, the case where the heat exchanger 4 is disposed in an inclined manner means that the air passage surface of the heat exchanger 4 is disposed so as to extend obliquely with respect to the partition plate 41.

  1 to 17, the heat source unit 1a-1 in which the compressor 1 is incorporated has been described as an example. However, the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, the drain pan The layout of FIG. 8 is not limited to the illustrated one.

Embodiment 2. FIG.
The second embodiment of the present invention will be described below. In the second embodiment, the description of the same parts as those in the first embodiment is omitted, and the same or corresponding parts as those in the first embodiment are denoted by the same reference numerals.

  FIG. 18 is a schematic top view schematically showing a state in which the heat source unit 1a-2, which is one of the heat exchange units according to Embodiment 2 of the present invention, is viewed from above. Hereinafter, based on FIG. 18, the heat source machine 1a-2 is demonstrated. In addition, in FIG. 18, the inside of the heat-source equipment 1a-2 is shown typically. In FIG. 18, the right side of the drawing is the rear surface of the heat source unit 1 a-2, the left side of the drawing is the front side of the heat source unit 1 a-2, the upper side of the page is the first side of the heat source unit 1 a-2, and the lower side of the page is the heat source unit. The state made into the 2nd side surface of 1a-2 is shown as an example.

  In the first embodiment, the case where the heat exchanger 4 is arranged so as to face the front surface of the heat source unit 1a-1 has been described as an example. However, in the second embodiment, the heat exchanger 4 is disposed around the centrifugal fan 3. It is arranged so as to surround it. Moreover, in Embodiment 1, although the blower outlet 10 is formed in the downstream position of the heat exchanger 4, ie, the front surface of the heat source machine 1a-1, in Embodiment 2, the blower outlet 10 is formed in arbitrary surfaces. It is possible.

  Specifically, the heat exchanger 4 includes a rear surface of the heat source unit 1a-2, a front surface of the heat source unit 1a-2, a first side surface of the heat source unit 1a-2, and a second side surface of the heat source unit 1a-2. It arrange | positions so that it may oppose. By arranging the heat exchanger 4 so as to surround the centrifugal fan 3, the rear surface of the heat source unit 1a-2, the front surface of the heat source unit 1a-2, the first side surface of the heat source unit 1a-2, and the heat source unit 1a. The blower outlet 10 can be formed on at least one of the second side surfaces of -2. Therefore, according to the heat source device 1a-2, the heat exchanger 4 can be mounted with high density, and the heat exchange efficiency can be improved.

  In addition, according to the experiments and analysis by the inventors, in order to efficiently mount the heat exchanger in a thin casing having the smallest height dimension among the height, width, and depth dimensions of the casing. Found that it is important to increase the front area of the heat exchanger. In other words, by increasing the front area of the heat exchanger, the resistance of the air passing through the heat exchanger can be reduced, and the air volume when the centrifugal fan 3 is rotated at an arbitrary rotational speed can be increased. is there.

  For this reason, arranging the heat exchanger 4 so as to surround the centrifugal fan 3 is more effective than increasing the mounting area of the heat transfer area by increasing the row pitch of the heat exchanger or by arranging multiple rows of heat exchangers. Thus, the heat exchange efficiency can be improved. Therefore, disposing the heat exchanger 4 so as to surround the centrifugal fan 3 increases the front surface area of the heat exchanger 4, so that heat exchange is performed while increasing the degree of freedom of installation of the air outlet 10. Efficiency can be improved effectively.

  Here, the case where the flow of air is seen from the upper surface will be described. FIG. 19 is a schematic top view schematically showing a state of an example of the heat source device 1a-2 as viewed from above. FIG. 20 is a schematic top view schematically showing a state in which another example of the heat source device 1a-2 is viewed from above. FIG. 21 is a schematic top view schematically illustrating a state of still another example of the heat source device 1a-2 as viewed from above. FIG. 22 is a schematic top view schematically illustrating a state of still another example of the heat source device 1a-2 as viewed from above. In FIGS. 19 to 22, the case where the air inlet 7 is formed on the rear surface of the housing 5 is illustrated as an example.

  In addition, in FIGS. 19-22, the inside of heat-source equipment 1a-2 is shown typically. Moreover, in FIGS. 19-22, the flow of air is represented by arrow A3 and arrow A4. Further, in FIGS. 19 to 22, the right side of the page is the rear surface of the heat source unit 1 a-2, the left side of the page is the front side of the heat source unit 1 a-2, and the upper side of the page is the first side of the heat source unit 1 a-2. Is shown as an example in a state in which the second side surface of the heat source unit 1a-2.

  In the housing 5 shown in FIG. 19, the air inlet 7 is formed on the rear surface of the housing 5, and the air outlet 10 is formed on the front of the housing 5. In this case, as shown by an arrow A3 in FIG. 19, air is taken in from the rear surface of the housing 5, passes through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4, and then blown out from the front of the housing 5. The

  In the housing 5 shown in FIG. 20, the air inlet 7 is formed on the rear surface of the housing 5, and the air outlet 10 is formed on the first side surface of the housing 5. In this case, as indicated by an arrow A3 in FIG. 20, air is taken in from the rear surface of the housing 5, passes through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4, and then from the first side surface of the housing 5. Blown out.

  In the housing 5 shown in FIG. 21, the air inlet 7 is formed on the rear surface of the housing 5, and the air outlet 10 is formed on the second side surface of the housing 5. In this case, as shown by an arrow A3 in FIG. 21, air is taken in from the rear surface of the housing 5, passes through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4, and then from the second side surface of the housing 5. Blown out.

  In the housing 5 shown in FIG. 22, the air inlet 7 is formed on the rear surface of the housing 5, and the air outlet 10 is formed on the rear surface of the housing 5. In this case, as shown by an arrow A3 in FIG. 22, air is taken in from the rear surface of the housing 5 and is blown out from the rear surface of the housing 5 after passing through the bell mouth 40, the centrifugal fan 3, and the heat exchanger 4. The

  As described above, by disposing the heat exchanger 4 so as to face the four surfaces of the housing 5, the air outlet 10 can be installed on any surface, and the degree of freedom in installing the air outlet 10 is greatly increased. Can be improved. Moreover, the blower outlet 10 is not limited to arrange | positioning in any surface, You may arrange | position to multiple surfaces or all the surfaces as needed. Furthermore, the air inlet 7 may be provided on the side surface having the largest area among the four side surfaces of the housing 5, the front surface, the first side surface, the second side surface, and the rear surface. In this case, the air path resistance of the intake port 7 becomes smaller.

  Here, the case where the flow of air is seen from the side will be described. FIG. 23 is a schematic cross-sectional view schematically showing an example of the AA cross section of FIG. In FIG. 23, the air flow is represented by arrows A1 and A2. Further, FIG. 23 shows an example in which the right side of the drawing is the rear surface of the heat source unit 1a-2 and the left side of the drawing is the front side of the heat source unit 1a-2.

  As shown in FIG. 23, the control box 2 may be a control box 2 having a low height so as not to close the outlet 10. That is, the control box 2 may be configured to be lower than the opening height of the outlet 10. Further, according to the analysis by the inventors, it has been found that the loss decreases when the heat exchanger 4 and the control box 2 are at least 50 mm apart. Therefore, the distance L between the heat exchanger 4 and the control box 2 is 50 mm or more, preferably 100 mm or more.

Next, a modified example of the arrangement of the heat exchanger 4 will be described.
FIG. 24 is a schematic top view schematically illustrating a state of an example of the heat source device 1a-2 as viewed from above. FIG. 25 is a schematic top view schematically showing a state when another example of the heat source device 1a-2 is viewed from above. FIG. 26 is a schematic top view schematically illustrating a state of still another example of the heat source device 1a-2 as viewed from above. 24 to 26 illustrate an example in which the air inlet 7 is formed on the first side surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5.

  Although FIGS. 19 to 23 show an example in which the heat exchanger 4 is disposed at positions facing the four sides of the side surface of the housing 5 so as to surround the centrifugal fan 3, the present invention is not limited to this. For example, the heat exchanger 4 may be arranged at a position facing two of the side surfaces of the housing 5 as shown in FIG. 24 or FIG. 25, and the heat exchanger 4 is placed in the housing 5 as shown in FIG. You may arrange | position in the position which opposes three surfaces among these side surfaces.

As shown in FIG. 24 or FIG. 25, in the case where the heat exchanger 4 is arranged in two surfaces, the surfaces on which the blower outlet 10 can be installed are two surfaces. That is, in FIG. 24, the front surface and the rear surface of the housing 5 are surfaces on which the air outlet 10 can be installed. In FIG. 25, the front surface and the first side surface of the housing 5 are surfaces on which the air outlet 10 can be installed.
As shown in FIG. 26, in the case where the heat exchanger 4 has a three-surface arrangement, there are three surfaces on which the air outlet 10 can be installed. That is, in FIG. 26, the front surface, the first side surface, and the second side surface of the housing 5 are surfaces on which the air outlet 10 can be installed.

  As described above, the greater the number of heat exchangers 4 arranged, the higher the degree of freedom for installing the air outlet 10. When the heat exchanger 4 has a two-sided or three-sided arrangement, the air path resistance can be reduced by arranging the heat exchanger 4 on the surface where the control box 2 and the compressor 1 are not installed. Is possible.

  18 to 26, the heat source unit 1a-2 in which the compressor 1 is incorporated has been described as an example. However, the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, the drain pan The layout of FIG. 8 is not limited to the illustrated one.

Embodiment 3 FIG.
The third embodiment of the present invention will be described below. In the third embodiment, the description of the same parts as those in the first and second embodiments is omitted, and the same or corresponding parts as those in the first and second embodiments are denoted by the same reference numerals. To do.

  FIG. 27 is a schematic top view schematically showing a state of an example of the heat source unit 1a-3, which is one of the heat exchange units according to Embodiment 3 of the present invention, viewed from above. FIG. 28 is a schematic top view schematically illustrating a state of another example of the heat source device 1a-3 as viewed from above. Hereinafter, based on FIG.27 and FIG.28, the heat source machine 1a-3 is demonstrated. In addition, in FIG.27 and FIG.28, the inside of the heat-source equipment 1a-3 is typically shown. 27 and 28, the right side of the paper is the rear surface of the heat source unit 1a-3, the left side of the page is the front side of the heat source unit 1a-3, the upper side of the page is the first side surface of the heat source unit 1a-3, and the lower side of the page. Is shown as an example in a state in which the second side surface of the heat source unit 1a-3. Furthermore, in FIG.27 and FIG.28, the flow of air is represented by the arrow.

  In the first embodiment and the second embodiment, the case where one centrifugal fan 3 is installed in the housing 5 has been described as an example. However, in the third embodiment, a plurality of centrifugal fans 3 are installed in the housing 5. Yes. 27 and 28, one centrifugal fan 3 on the upper side of the drawing among the plurality of centrifugal fans 3 is defined as a first centrifugal fan 3a, and the other centrifugal fan 3 on the lower side of the drawing among the plurality of centrifugal fans 3 is a second centrifugal. It is illustrated as a fan 3b.

  Even if the housing 5 has a rectangular shape in top view, high performance can be obtained by providing a plurality of centrifugal fans 3. As shown in FIGS. 27 and 28, in the case of the case 5 having a rectangular shape when viewed from above, the first centrifugal fan 3a and the second centrifugal fan 3b are arranged in the case 5 so as to be aligned in the long side direction, that is, the width direction. That's fine.

When a plurality of centrifugal fans 3 are provided, a fan partition plate 11 may be provided between the centrifugal fans 3. By providing the fan partition plate 11, interference between the centrifugal fans 3 can be suppressed.
The fan partition plate 11 corresponds to a “third partition plate”.
Furthermore, by using the casing 5 having a rectangular shape in a top view as shown in FIGS. 27 and 28, the air path blockage portion of the control box 2 on the rear surface of the casing 5 can be made relatively small. In addition, the heat exchanger 4 can be mounted in the width direction of the housing 5 by an amount corresponding to the increased width.

  In addition, the rotation direction of the plurality of centrifugal fans 3 is not particularly limited. However, when the centrifugal fans 3 are rotated in the opposite directions, the interference of the air currents of the centrifugal fans 3 can be suppressed, and the energy efficiency can be improved. .

In FIG. 27, the first centrifugal fan 3a and the second centrifugal fan 3b are positioned so that the center point of the first centrifugal fan 3a and the center point of the second centrifugal fan 3b are on the same straight line parallel to the width direction of the housing 5. A case where the second centrifugal fan 3b is arranged is illustrated as an example.
In FIG. 28, the first centrifugal fan 3 a and the first centrifugal fan 3 a and the second centrifugal fan 3 b and the first centrifugal fan 3 a and the second centrifugal fan 3 b are located on different straight lines parallel to the width direction of the housing 5. A case where two centrifugal fans 3b are arranged is illustrated as an example. For example, the center point A of the first centrifugal fan 3 a may be located on the rear side of the housing 5, and the center point B of the second centrifugal fan 3 b may be located on the front side of the housing 5.

  When the plurality of centrifugal fans 3 are arranged at positions as shown in FIG. 28, the second centrifugal fan 3 b in which a part of the air path is blocked by the compressor 1 and the control box 2 is removed from the compressor 1 and the control box 2. It can be arranged at a distant position, that is, on the front side of the housing 5. By separating the centrifugal fan 3 from the air path resistors such as the compressor 1 and the control box 2, aerodynamic loss, abnormal noise, and noise can be suppressed.

  27 and 28, the heat source unit 1a-3 in which the compressor 1 is built is described as an example, but the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, the drain pan The layout of FIG. 8 is not limited to the illustrated one.

Embodiment 4 FIG.
Embodiment 4 of the present invention will be described below. In the fourth embodiment, the description overlapping with the first to third embodiments will be omitted, and the same or corresponding parts as those in the first to third embodiments will be denoted by the same reference numerals. To do.
In the fourth embodiment, it is assumed that the inlet port 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5, including modifications. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  FIG. 29 is a schematic top view schematically showing a state of an example of the heat source device 1a-4, which is one of the heat exchange units according to Embodiment 4 of the present invention, as viewed from above. FIG. 30 is a schematic cross-sectional view schematically showing an example of the AA cross section of FIG. 29. Hereinafter, based on FIG.29 and FIG.30, the heat source machine 1a-4 is demonstrated. In addition, in FIG. 29, the inside of the heat-source equipment 1a-4 is shown typically. 29, the right side of the paper is the rear surface of the heat source unit 1a-4, the left side of the page is the front surface of the heat source unit 1a-4, the upper side of the page is the first side surface of the heat source unit 1a-4, and the lower side of the page is the heat source unit. The state made into the 2nd side surface of 1a-4 is shown as an example. Furthermore, in FIG. 29, the flow of air is represented by arrows. In FIG. 30, the air flow is indicated by arrows A1 and A2.

  In FIG. 29, the case where the several centrifugal fan 3 is installed in the housing | casing 5 is illustrated as an example. However, the number of installed centrifugal fans 3 may not be plural. In FIG. 29, one centrifugal fan 3 on the upper side of the drawing among the plurality of centrifugal fans 3 is a first centrifugal fan 3a, and the other centrifugal fan 3 on the lower side of the drawing among the plurality of centrifugal fans 3 is a second centrifugal fan 3b. It is shown. Note that the number of centrifugal fans 3 may be one as in the first embodiment or the second embodiment.

  Moreover, in Embodiment 4, as shown in FIG. 29, the heat exchanger 4 is arrange | positioned in the position facing the four surfaces of the housing | casing 5 so that the 1st centrifugal fan 3a and the 2nd centrifugal fan 3b may be enclosed. Since the fan partition plate 11 is disposed on the lower side of the first centrifugal fan 3a and the upper side of the second centrifugal fan 3b, the heat exchanger 4 does not exist. In addition, in FIG. 30, the heat exchanger 4 arrange | positioned in the position which opposes the front of the housing | casing 5 in the state which looked at the heat-source equipment 1a-4 in cross section is illustrated as the heat exchanger 4a, The heat exchanger 4 arranged at the opposite position is shown as a heat exchanger 4b.

In the fourth embodiment, a bypass air passage 6 is provided inside the housing 5. Specifically, in the heat source device 1a-4, the bypass air passage 6 is formed inside the housing 5 by providing the bypass partition plate 9 inside the housing 5 as shown in FIG. The bypass partition plate 9 is provided so as to extend parallel to the partition plate 41 at the upper position of the heat exchanger 4. The bypass air passage 6 guides the air blown out from the centrifugal fan 3 and passed through a part of the heat exchanger 4 directly to the air outlet 10. By providing the bypass air passage 6, it is possible to allow a large amount of air to flow into the heat exchanger 4 b that is located away from the air outlet 10 and is located at a position where the wind does not easily flow.
The bypass partition plate 9 corresponds to a “second partition plate”.

  In FIG. 30, the height of the bypass air passage 6 is illustrated as a height H3. Specifically, the height H <b> 3 represents the distance between the bypass partition plate 9 and the upper surface of the housing 5. Further, the height of the housing 5 is illustrated as a height H1. Specifically, the height H <b> 1 represents the distance between the upper surface of the housing 5 and the lower surface of the housing 5.

  FIG. 31 is a graph illustrating an example of an analysis result when the bypass air passage 6 is provided. FIG. 31 shows the relationship between H3 / H1, which is the ratio of height H3 and height H1, and energy efficiency. In FIG. 31, the vertical axis represents energy efficiency (%), and the horizontal axis represents H3 / H1 (%).

  From FIG. 31, it was found that a relatively high energy efficiency can be obtained in a wide range by setting the height H3 in a range where H3 / H1 is 40% or less. It has also been found that when H3 / H1 is provided in an amount of more than 40%, the energy efficiency is rapidly reduced. It was also found that the energy efficiency decreases with a peak value of H3 / H1 of 40% or less. Therefore, energy efficiency of 70% or more can be obtained by setting the range of H3 / H1 to a range of preferably 10% to 40%.

Next, a modified example of the arrangement of the heat exchanger 4 will be described.
FIG. 32 is a schematic top view schematically illustrating a state of an example of the heat source device 1a-4 as viewed from above.

  In FIG. 29, the case where the heat exchanger 4 is arranged at a position facing the four surfaces of the housing 5 is shown as an example, but in FIG. 32, the heat exchanger 4 is arranged at a position facing the two surfaces of the housing 5. The case is shown as an example. Specifically, the heat exchanger 4 is arranged at a position facing the front surface of the housing 5 and a position facing the rear surface of the housing 5 in correspondence with the formation positions of the air inlet 7 and the air outlet 10. That is, the bypass air passage 6 can be effective not only in arranging the heat exchanger 4 on four sides but also in a layout in which the heat exchanger 4 is arranged on two sides as shown in FIG.

  In FIGS. 29 to 32, the heat source unit 1 a-4 in which the compressor 1 is incorporated has been described. However, the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, The layout of the drain pan 8 is not limited to the illustrated one.

Embodiment 5 FIG.
The fifth embodiment of the present invention will be described below. In the fifth embodiment, the description of the same parts as those in the first to fourth embodiments is omitted, and the same or corresponding parts as those in the first to fourth embodiments are denoted by the same reference numerals. To do.
In the fifth embodiment, it is assumed that the air inlet 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  33 is a schematic cross-sectional view schematically showing an example of a heat source machine 1a-5, which is one of the heat exchange units according to Embodiment 5 of the present invention, corresponding to the AA cross section of FIG. FIG. 33 shows an example in which the right side of the drawing is the rear surface of the heat source unit 1a-4 and the left side of the drawing is the front side of the heat source unit 1a-4. In FIG. 33, the air flow is indicated by arrows A1 and A2.

  In the fifth embodiment, the bypass air passage 6 is provided inside the housing 5, and a part of the fan motor 13 provided in the upper part of the centrifugal fan 3 projects into the bypass air passage 6. As described in the fourth embodiment, the provision of the bypass air passage 6 makes it easy for air to flow also to the heat exchanger 4 on the rear surface side disposed at a position away from the outlet 10. Therefore, sufficient air is convected through the bypass air passage 6. For this reason, by projecting a part of the fan motor 13 to the bypass air passage 6, the fan motor 13 can be cooled using the convection of the air flowing through the bypass air passage 6, and the quality can be improved. it can.

  Further, by providing a cooling function by convection, it is possible to reduce the number of cooling members and accompanying parts, and to simplify the structure. On the other hand, when the heat exchanger 4 functions as a condenser for heating air, the air can be heated by the exhaust heat of the fan motor 13, and the energy efficiency can be improved accordingly.

  In addition, in FIG. 33, although demonstrated supposing the heat source machine 1a-5 in which the compressor 1 was incorporated, the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, the drain pan 8 The layout and the like are not limited to those illustrated.

Embodiment 6 FIG.
The sixth embodiment of the present invention will be described below. In the sixth embodiment, the description of the same parts as those in the first to fifth embodiments is omitted, and the same or corresponding parts as those in the first to fifth embodiments are denoted by the same reference numerals. To do.
In the sixth embodiment, it is assumed that the air inlet 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  FIG. 34 is a schematic top view schematically showing a state when one example of the heat source unit 1a-6, which is one of the heat exchange units according to Embodiment 6 of the present invention, is viewed from above. FIG. 35 is a schematic cross-sectional view schematically showing an example of the AA cross section of FIG. 34. FIG. 36 and FIG. 37 are schematic views schematically showing an example of the heat exchanger 4 as viewed from the cross section side. Hereinafter, based on FIGS. 34-37, the heat source machine 1a-6 is demonstrated. In addition, in FIG. 34, the inside of the heat source machine 1a-6 is typically shown. 34, the right side of the paper is the rear surface of the heat source unit 1a-6, the left side of the page is the front side of the heat source unit 1a-6, the upper side of the page is the first side of the heat source unit 1a-6, and the lower side of the page is the heat source unit. The state made into the 2nd side surface of 1a-6 is shown as an example. Furthermore, in FIG.34 and FIG.36, the flow of air is represented by the arrow. In FIG. 35, the air flow is indicated by arrows A1 and A2.

  In the sixth embodiment, as shown in FIG. 34, the heat exchanger 4 is disposed at a position facing the four surfaces of the housing 5 so as to surround the first centrifugal fan 3a and the second centrifugal fan 3b. Since the fan partition plate 11 is disposed on the lower side of the first centrifugal fan 3a and the upper side of the second centrifugal fan 3b, the heat exchanger 4 does not exist.

In the sixth embodiment, at least one surface of the heat exchanger 4 disposed on at least two surfaces, here, the heat exchanger 4 disposed on the front surface is disposed so as to have a V-shape in a lateral view in cross section. Yes. The heat exchanger 4 disposed opposite to the remaining three surfaces, that is, the rear surface, the first side surface, and the second side surface is a heat exchanger 4 having a linear shape in cross section.
34 and 35, the heat exchanger 4 disposed on the front side of the housing 5 is disposed so as to have a V shape in the cross-sectional view. In FIGS. 34 and 35, the heat exchanger 4 arranged in a V-shape in the cross-sectional view is distinguished as the heat exchanger 22 and illustrated.

  That is, the heat exchanger 22 and the heat exchanger 4 are arranged in the housing 5 so as to surround the centrifugal fan 3. The heat exchanger 4 can be mounted with high density by arranging the V-shaped heat exchanger 22 in a cross-sectional view sideways on a part of the surface of the housing 5. That is, even if the housing 5 is thin, the heat exchanger 4 can be mounted at a high density, so that the heat exchange efficiency can be improved, and further the energy efficiency can be improved.

  Also in the sixth embodiment, the bypass air passage 6 is provided inside the housing 5. In FIG. 34, the case where the several centrifugal fan 3 is installed in the housing | casing 5 is illustrated as an example. However, the number of installed centrifugal fans 3 may not be plural. In FIG. 34, the one on the upper side of the drawing among the plurality of centrifugal fans 3 is illustrated as the first centrifugal fan 3a, and the one on the lower side of the drawing among the plurality of centrifugal fans 3 is illustrated as the second centrifugal fan 3b. As in the first embodiment or the second embodiment, the number of centrifugal fans 3 may be one. Further, in the heat source device 1a-6, the bypass air passage 6 is formed inside the housing 5 by providing the bypass partition plate 9 inside the housing 5 as shown in FIG.

The flow of air in the heat exchanger 22 will be described.
As shown in FIG. 36, in the heat exchanger 22, air hardly flows in a region C in the vicinity of the joint between the heat exchanger on the upper side of the paper and the heat exchanger on the lower side of the paper. Therefore, the ventilation resistance is generally larger than that of the linear heat exchanger 4 as shown in FIG. Therefore, by disposing the V-shaped heat exchanger 22 in the side view in the heat exchanger 4 close to the blower outlet 10, a large amount of air can flow through the heat exchanger 4 located at a position away from the blower outlet 10. Become.
Moreover, when the bypass air passage 6 is provided, the height of the bypass air passage 6 can be reduced by disposing the heat exchanger 22 having a V shape in a side view at a position close to the air outlet 10. .

A modification of the arrangement of the heat exchanger 4 will be described.
FIG. 38 is a schematic view schematically showing a state in which another example of the arrangement of the heat exchanger 4 is viewed in cross section. In FIG. 38, the air flow is indicated by arrows. Further, in FIG. 38, the heat exchangers 4 that are inclined in a cross-sectional view are shown as being distinguished as the heat exchangers 23.

  As shown in FIG. 38, one heat exchanger 4 may be disposed in an inclined manner. For example, as shown in FIG. 38, the heat exchanger 23 is disposed so as to descend from the left side to the right side. The case where the heat exchanger 4 is disposed in an inclined manner means that the air passage surface of the heat exchanger 4 is disposed so as to extend obliquely with respect to the partition plate 41. Note that the heat exchanger 4 may be inclined so as to rise from the left side to the right side.

As shown in FIG. 38, by arranging the heat exchanger 23 in an inclined manner, the heat exchanger can be mounted at a high density within the limited height restriction inside the housing 5. Therefore, the heat exchange efficiency can be improved by adopting the arrangement as shown in FIG.
As shown in FIG. 38, since the air flow in the heat exchanger 23 bends obliquely, the ventilation resistance is larger than that of the heat exchanger 4 having a linear shape in cross section. For this reason, when the heat exchanger 23 is disposed at a position close to the air outlet 10 and the heat exchanger 4 having a linear shape in cross section is disposed at a position away from the air outlet 10, the distribution of the air flow amount flowing through each heat exchanger is Can be improved.

  36 and 38, the inclination angle of the heat exchanger 4 is set so that the distance between the tip of the centrifugal fan 3 and the heat exchanger 4 can be increased according to the height position of the centrifugal fan 3. And the inclination direction may be selected.

  34 to 38 have been described assuming the heat source unit 1a-6 in which the compressor 1 is built, the presence or absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, The layout of the drain pan 8 is not limited to the illustrated one.

Embodiment 7 FIG.
The seventh embodiment of the present invention will be described below. In the seventh embodiment, the description overlapping with that of the first to sixth embodiments is omitted, and the same or corresponding parts as those of the first to sixth embodiments are denoted by the same reference numerals. To do.
In the seventh embodiment, it is assumed that the air inlet 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  FIG. 39 is a schematic top view schematically showing a state when one example of the heat source unit 1a-7, which is one of the heat exchange units according to Embodiment 7 of the present invention, is viewed from above. In FIG. 39, the right side of the drawing is the rear surface of the heat source unit 1a-7, the left side of the drawing is the front side of the heat source unit 1a-7, the upper side of the page is the first side of the heat source unit 1a-7, and the lower side of the page is the heat source unit. The state made into the 2nd side surface of 1a-7 is shown as an example. In FIG. 39, the air flow is indicated by arrows.

  In Embodiment 7, the heat exchanger 4 is arrange | positioned so that each centrifugal fan 3 may be enclosed in the form using the some centrifugal fan 3. FIG. For example, when two centrifugal fans 3 are used, the heat exchanger 4 is arranged in the shape of glasses as viewed from above.

  By disposing the heat exchanger 4 so as to surround each centrifugal fan 3, the heat exchanger 4 can be mounted with high density. That is, even if the housing 5 is thin, the heat exchanger 4 can be mounted at a high density, so that the heat exchange efficiency can be improved, and further the energy efficiency can be improved.

  Here, as an example, an example is shown in which each centrifugal fan 3 is disposed so as to be surrounded by an O-shape when viewed from above. However, the present invention is not limited to this. Any visual shape may be used. For example, in the case where a plurality of centrifugal fans 3 are arranged, the control box 2 may be arranged such that the center thereof is located at the center between the centrifugal fans 3. By doing so, the air volume ratio of the air between the centrifugal fans 3 due to the blockage of the air path of the control box 2 can be made closer to each centrifugal fan 3 evenly.

  39, the heat source unit 1a-7 in which the compressor 1 is incorporated has been described. However, the presence / absence of the compressor 1 and the control box 2, the arrangement of the compressor 1 and the control box 2, the drain pan 8 The layout and the like are not limited to those illustrated.

Embodiment 8 FIG.
Embodiment 8 of the present invention will be described below. In the eighth embodiment, the description of the same parts as those in the first to seventh embodiments is omitted, and the same or corresponding parts as those in the first to seventh embodiments are denoted by the same reference numerals. To do.
In the eighth embodiment, it is assumed that the intake port 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5, including modifications. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  FIG. 40 is a schematic top view schematically showing a state of an example of a heat source machine that is one of the heat exchange units according to Embodiment 8 of the present invention, viewed from above. FIG. 41 is a schematic cross-sectional view schematically showing an example of the AA cross-section of FIG. Hereinafter, based on FIG.40 and FIG.41, the heat source machine 1a-8 is demonstrated. In addition, in FIG. 40, the inside of the heat source machine 1a-8 is typically shown. 40, the right side of the paper is the rear surface of the heat source machine 1a-8, the left side of the paper is the front surface of the heat source machine 1a-8, the upper side of the paper is the first side of the heat source machine 1a-8, and the lower side of the paper is the heat source machine. The state made into the 2nd side surface of 1a-8 is shown as an example. Further, in FIG. 41, the air flow is indicated by arrows A1 and A2.

  As shown in FIG. 41, an intake air passage 14A is provided in the space below the fan intake port 45 of the centrifugal fan 3 so as to reach the rear surface. As shown in FIGS. 40 and 41, a blowout air passage 42 is provided on the downstream side of the centrifugal fan 3, and the blowout air passage 42 and the intake air passage 14 </ b> A are partitioned by a suction blowout partition plate 43. Yes. With such a configuration, the rear space of the centrifugal fan 3 and the housing 5 can be secured widely, and the air blown to the rear side of the centrifugal fan 3 (surface far from the outlet 10) can be efficiently used. Can be passed through the heat exchanger 4. As a result, the heat exchange efficiency is improved.

  In particular, when the centrifugal fan 3 is mounted in the housing at a high density, if the outer periphery of the centrifugal fan 3 is too close to the rear surface of the housing 5, it causes a sudden increase in ventilation resistance. FIG. 42 is a diagram for explaining the relationship between the position of the centrifugal fan and the ventilation resistance in the heat exchange unit according to Embodiment 8 of the present invention. As shown in FIG. 42, the radius of the centrifugal fan 3 is defined as r, and the distance from the rotation center axis Ax of the centrifugal fan 3 to the rear surface of the housing 5 is defined as x. FIG. 43 is a graph showing an example of the experimental results of the inventors. FIG. 43 is a graph showing an example of the relationship between the distance from the rotation center axis of the centrifugal fan to the rear surface, the ratio of the fan radius, and the ventilation resistance in the heat exchange unit according to Embodiment 8 of the present invention. The horizontal axis in FIG. 43 is the ratio value (x / r), and the vertical axis in FIG. 43 is the ventilation resistance. Referring to the experimental results shown in FIG. 43, in the range where the ratio value (x / r) is 1.05 or less, the ventilation resistance increases rapidly. Therefore, the distance x is preferably a value at which the ratio value (x / r) is larger than 1.05. The ratio value (x / r) is preferably 1.10 or more.

  As shown in FIGS. 40 and 41, the front surface area of the heat exchanger 4 arranged around the blowout air passage 42 is increased by configuring the intake air passage 14A so as not to reach the front surface of the housing 5. can do. Therefore, the air blown to the rear surface side (surface far from the blower outlet 10) of the centrifugal fan 3 can be passed through the heat exchanger 4 efficiently. As a result, the heat exchange efficiency is improved.

  Further, the heat source machine 1a-8 of the eighth embodiment includes a V-shaped heat exchanger 4 that is laterally viewed in cross section. The heat exchanger 4 includes an upper heat exchanger 22a and a lower heat exchanger 22b. As shown in FIG. 42, the heat exchanger 22 a is disposed so as to be inclined by an angle θ with respect to a direction horizontal to the blowing air passage 42. FIG. 42 shows that the heat exchanger 22a is inclined by the angle θ with respect to the air blowing direction, but the heat exchanger 22b is also inclined by the angle θ with respect to the air blowing direction. Good. The inclination angle θ of the heat exchanger 22a is an elevation angle with respect to the horizontal direction, whereas the inclination angle θ of the heat exchanger 22b is a depression angle with respect to the horizontal direction. By disposing at least one of the heat exchangers 22a and 22b with an inclination, the front area of the heat exchanger 4 can be increased. Therefore, the air blown to the rear surface side (surface far from the blower outlet 10) of the centrifugal fan 3 can be passed through the heat exchanger 4 efficiently. As a result, the heat exchange efficiency is improved.

  FIG. 44 shows an example of the experimental results of the inventors. FIG. 44 is a graph showing an example of the relationship between the inclination angle of the heat exchanger and the ventilation resistance in the heat exchange unit according to Embodiment 8 of the present invention. Also in this experiment, the casing 5 having a height of 500 mm or less was used. 44, when the heat exchangers 22a and 22b are arranged so that the inclination angle θ is 30 ° or more when the height of the housing 5 is 500 mm or less, the ventilation of the heat exchanger 4 is achieved. Resistance is suppressed. Therefore, the air circulation efficiency is improved.

FIG. 45 is a diagram schematically showing another example of the heat exchanger according to Embodiment 8 of the present invention corresponding to the AA cross section of FIG. 40. Heat exchanger 4 shown in FIG. 45, based on the horizontal direction in outlet air passage 42, the configuration and the inclination angle theta ₂ of the upper heat exchanger 22a, and the inclination angle theta ₁ of the lower heat exchanger 22b different It is. By arranging the heat exchanger 4 so that the inclination angle θ ₂ and the inclination angle θ ₁ are different, the ventilation resistance of the heat exchanger 4 can be adjusted. Therefore, the air circulation efficiency in the heat exchanger 4 can be adjusted. Furthermore, the end of the heat exchanger 4 can be separated from the centrifugal fan 3 by making the relationship of the inclination angle θ ₂ > the inclination angle θ ₁ . Therefore, the air blown out from the centrifugal fan 3 toward the rear surface can easily pass through the heat exchanger 4. As a result, the air circulation efficiency in the heat exchanger 4 is further improved.

  FIG. 46 is a diagram schematically showing another example of the heat exchanger according to Embodiment 8 of the present invention corresponding to the AA cross section of FIG. 40. The configuration example shown in FIG. 46 is characterized in that the length Lk1 of the upper heat exchanger 22a is longer than the length Lk2 of the lower heat exchanger 22b in the V-shaped heat exchanger 4 that is laterally viewed in cross section. And By setting it as such a structure, the space of the upper part of the centrifugal fan 3 can be used effectively as an installation space of the heat exchanger 22a, and the front surface area of the heat exchanger 4 can be enlarged. Therefore, the heat exchange efficiency is improved.

Embodiment 9 FIG.
Embodiment 9 of the present invention will be described below. In the ninth embodiment, the description overlapping with that of the first to eighth embodiments is omitted, and the same or corresponding parts as those of the first to eighth embodiments are denoted by the same reference numerals. To do.
In the ninth embodiment, it is assumed that the air inlet 7 is formed on the rear surface of the housing 5 and the air outlet 10 is formed on the front surface of the housing 5. However, the formation positions of the air inlet 7 and the air outlet 10 are not particularly limited.

  FIG. 47 is a schematic top view schematically showing a state when one example of the load side machine 2a, which is one of the heat exchange units according to Embodiment 9 of the present invention, is viewed from above. 47, the right side of the page is the rear side of the load side machine 2a, the left side of the page is the front side of the load side machine 2a, the upper side of the page is the first side surface of the load side machine 2a, and the lower side of the page is the load side machine 2a. The state made into the 2nd side surface is shown as an example. In FIG. 47, the air flow is indicated by arrows. Furthermore, in FIG. 47, the load side unit 2a to which the housing layout of the heat source unit 1a-7 according to Embodiment 7 is applied is illustrated as an example.

  The load side machine 2a is one of heat exchange units including a heat exchanger, and constitutes an air conditioner together with the heat source apparatus according to any one of the first to eighth embodiments. And the load side machine 2a applies the housing layout of the heat source machine which concerns on either of Embodiment 1-8. In general, the load side machine 2a often does not include the compressor 1 and the control box 2. That is, the load side machine 2a is the same as the structure which remove | excluded the compressor 1 and the control box 2 from the heat source machine which concerns on either of Embodiment 1-8.

That is, in the load side machine 2a, it is not necessary to assume that the air path is blocked by the compressor 1 and the control box 2 in the first place. Therefore, it becomes possible to mount the heat exchanger 4 with high density.
In addition, in FIG. 47, although the structure which applied the housing | casing layout of the heat-source equipment 1a-7 which concerns on Embodiment 7 is shown as an example, in load side machine 2a, any of Embodiment 1- Embodiment 8 is shown. The housing layout of the heat source apparatus according to the above can be applied.

Embodiment 10 FIG.
The tenth embodiment of the present invention will be described below. In the tenth embodiment, the description overlapping with those in the first to ninth embodiments is omitted, and the same or corresponding parts as those in the first to ninth embodiments are denoted by the same reference numerals. To do. Note that the refrigerant circuit configurations shown in FIGS. 48 and 49 merely represent a general vapor compression refrigeration cycle, and the refrigerant circuit configuration of the air conditioner 100 is not limited thereto. Further, the heat exchanger 4 of the load side machine 2a is distinguished as the first heat exchanger 4-1, and the heat exchanger 4 of the heat source machine 1a-1 is distinguished as the second heat exchanger 4-2.

  48 and 49 are configuration diagrams schematically showing an example of the refrigerant circuit configuration of the air-conditioning apparatus 100 according to Embodiment 10 of the present invention. The air conditioning apparatus 100 will be described with reference to FIGS. 48 and 49. The air conditioning apparatus 100 includes at least one of the heat source device according to any one of the first to seventh embodiments and the load side device 2a according to the ninth embodiment. In addition, in FIG. 48, although the case where it has both the heat-source equipment 1a-1 which concerns on Embodiment 1, and the load side machine 2a which concerns on Embodiment 9 is shown as an example, it is limited to this. is not. The air conditioning apparatus 100 only needs to include at least one of the heat source device according to any one of the first to seventh embodiments and the load-side device 2a according to the ninth embodiment.

  48 and 49, the air conditioner 100 that can switch the flow of the refrigerant is illustrated as an example. In FIG. 48, when the first heat exchanger 4-1 functions as a condenser and the second heat exchanger 4-2 functions as an evaporator, that is, the refrigerant flow during the heating operation is indicated by an arrow. On the other hand, in FIG. 49, when the first heat exchanger 4-1 functions as an evaporator and the second heat exchanger 4-2 functions as a condenser, the refrigerant flow during the cooling operation is indicated by an arrow.

  The air conditioner 100 includes a compressor 1, a flow path switching device 25, a first heat exchanger 4-1, a decompression device 24, and a second heat exchanger 4-2 as main element devices. . As refrigerant pipes for connecting them, a first connection pipe 29, a second connection pipe 30, a third connection pipe 31, a fourth connection pipe 26, a fifth connection pipe 27, and a sixth connection pipe 28 are provided. . That is, the air conditioner 100 includes a refrigerant circuit in which the compressor 1, the flow path switching device 25, the first heat exchanger 4-1, the decompression device 24, and the second heat exchanger 4-2 are connected by refrigerant piping. I have.

  The first connection pipe 29 is a refrigerant pipe that connects the compressor 1 and the flow path switching device 25. The second connection pipe 30 is a refrigerant pipe that connects the flow path switching device 25 and the first heat exchanger 4-1. The third connection pipe 31 is a refrigerant pipe that connects the first heat exchanger 4-1 and the decompression device 24. The fourth connection pipe 26 is a refrigerant pipe that connects the decompression device 24 and the second heat exchanger 4-2. The fifth connection pipe 27 is a refrigerant pipe that connects the second heat exchanger 4-2 and the flow path switching device 25. The sixth connection pipe 28 is a refrigerant pipe that connects the flow path switching device 25 and the compressor 1.

  Here, a case where the flow path switching device 25 is provided and the flow of the refrigerant can be switched by the flow path switching device 25 is illustrated as an example, but the flow of the refrigerant is made constant without providing the flow path switching device 25. Also good. In this case, the first heat exchanger 4-1 functions only as a condenser, and the second heat exchanger 4-2 functions only as an evaporator.

The heat source device 1a-1 is installed in a space different from the air-conditioning target space, for example, outdoors, and has a function of supplying cold or warm heat to the load side device 2a.
The load-side unit 2a is installed in a space that supplies cold or hot air to the air-conditioning target space, for example, indoors, and cools or warms the air-conditioning target space by the cold or hot heat supplied from the heat source device 1a-1. Here, although the case where the decompression device 24 is provided in the heat source device 1a-1 is illustrated as an example, the decompression device 24 may be provided in the load side device 2a.

  The compressor 1 compresses and discharges the refrigerant. The compressor 1 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, or a reciprocating compressor. When the first heat exchanger 4-1 functions as a condenser, the refrigerant discharged from the compressor 1 is sent to the first heat exchanger 4-1. When the 1st heat exchanger 4-1 functions as an evaporator, the refrigerant discharged from compressor 1 is sent to the 2nd heat exchanger 4-2.

  The flow path switching device 25 is provided on the discharge side of the compressor 1 and switches the refrigerant flow between the heating operation and the cooling operation. The flow path switching device 25 can be configured by, for example, a combination of a four-way valve, a three-way valve, or a combination of two-way valves.

  The first heat exchanger 4-1 functions as a condenser or an evaporator, and can be configured by, for example, a fin-and-tube heat exchanger.

  The decompression device 24 decompresses the refrigerant that has passed through the first heat exchanger 4-1 or the second heat exchanger 4-2. The decompression device 24 can be composed of, for example, an electronic expansion valve. Further, the decompression device 24 may be constituted by a flow resistor in which a capillary tube and a valve are combined.

  The 2nd heat exchanger 4-2 functions as an evaporator or a condenser, and can comprise a fin and tube type heat exchanger, for example.

Based on FIG. 48, the operation | movement at the time of the heating operation of the air conditioning apparatus 100 is demonstrated with the flow of a refrigerant | coolant.
In the compressor 1, the refrigerant becomes high-temperature and high-pressure refrigerant superheated steam, passes through the first connection pipe 29 and the second connection pipe 30, and flows into the load side machine 2a. The refrigerant flowing into the load side machine 2a flows into the first heat exchanger 4-1 through the refrigerant distribution pipe 19, and exchanges heat with the air supplied by the centrifugal fan 3 in the first heat exchanger 4-1. And cooled. At this time, the indoor air passing through the first heat exchanger 4-1 is heated by the refrigerant, and is transported to an air-conditioning target space such as a living space, and the air-conditioning target space is warmed and heated.

  The refrigerant cooled by the first heat exchanger 4-1 flows out of the first heat exchanger 4-1 through the refrigerant collecting pipe 20 in the state of supercooled liquid or gas-liquid two-phase refrigerant. The refrigerant that has flowed out of the first heat exchanger 4-1 flows through the third connection pipe 31 and flows into the decompression device 24. In the decompression device 24, the refrigerant is squeezed and expanded, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. This refrigerant passes through the fourth connection pipe 26 and flows into the heat source unit 1a-1.

Based on FIG. 49, the operation | movement at the time of the cooling operation of the air conditioning apparatus 100 is demonstrated with the flow of a refrigerant | coolant.
In the compressor 1, the refrigerant becomes high-temperature and high-pressure refrigerant superheated steam, passes through the first connection pipe 29 and the fifth connection pipe 27, and flows into the heat source machine 1a-1. The refrigerant that has flowed into the heat source machine 1a-1 flows into the second heat exchanger 4-2 through the refrigerant collecting pipe 20, and the outside air and heat supplied by the centrifugal fan 3 in the second heat exchanger 4-2. Replace and cool. The refrigerant cooled by the second heat exchanger 4-2 flows out from the second heat exchanger 4-2 through the refrigerant distribution pipe 19 in the state of supercooled liquid or gas-liquid two-phase refrigerant. The refrigerant flowing out from the second heat exchanger 4-2 passes through the fourth connection pipe 26 and flows into the decompression device 24.

  In the decompression device 24, the refrigerant is squeezed and expanded, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. This refrigerant passes through the third connection pipe 31 and flows into the load side machine 2a. The refrigerant that has flowed into the load-side unit 2a receives heat from indoor air, for example. In other words, the room air is cooled and cooled. The refrigerant heated by the first heat exchanger 4-1 becomes a gas-liquid two-phase refrigerant or superheated steam having a high dryness, passes through the second connection pipe 30 and the sixth connection pipe 28, and is sucked into the compressor 1. The The refrigerant sucked into the compressor 1 is compressed again by the compressor 1 and discharged as high-temperature and high-pressure refrigerant superheated steam. Thereafter, this cycle is repeated.

  Therefore, the air conditioner 100 includes at least one of the heat source device according to any one of the first to seventh embodiments and the load-side device 2a according to the ninth embodiment. Therefore, the degree of freedom of installation can be greatly improved.

A modification of the air conditioner 100 will be described.
FIG. 50 is a configuration diagram schematically illustrating an example of a refrigerant circuit configuration of a modified example of the air-conditioning apparatus 100. Based on FIG. 50, the modification of the air conditioning apparatus 100 is demonstrated. In addition, the modification of the air conditioning apparatus 100 shall be distinguished as the air conditioning apparatus 100A.

The air conditioner 100A includes a gas-liquid separator 34 provided between the decompression device 24 and the second heat exchanger 4-2, and an outlet side of the gas-liquid separator 34 and the second heat exchanger 4-2. A connected bypass pipe 35 and at least one flow rate adjusting device 37 installed in the bypass pipe 35 are provided.
The gas-liquid separator 34 separates the refrigerant into a gas refrigerant and a liquid refrigerant. The gas refrigerant separated by the gas-liquid separator 34 is sent to the flow rate adjusting device 37. The liquid refrigerant separated by the gas-liquid separator 34 is sent to the second heat exchanger 4-2. The bypass pipe 35 is a refrigerant pipe that guides the gas refrigerant separated by the gas-liquid separator 34 to the outlet of the second heat exchanger 4-2. The flow rate adjusting device 37 adjusts the flow rate of the refrigerant flowing through the bypass pipe 35.

  The gas-liquid separator 34 is provided on the upstream side of the refrigerant flow during the heating operation of the second heat exchanger 4-2, and the opening degree of the flow rate adjusting device 37 is controlled during the heating operation. The refrigerant can be supplied to the refrigerant distribution pipe 19 of the second heat exchanger 4-2 in the refrigerant state, and the distribution performance is improved. In addition, by bypassing excess gas refrigerant that does not contribute to heat exchange, pressure loss in the second heat exchanger 4-2 can be reduced, and energy efficiency can be improved.

  During the cooling operation, the gas-liquid separator 34 functions as a liquid reservoir, and exhibits an effect of reducing the difference in the optimum refrigerant charging amount between the cooling operation and the heating operation. Furthermore, by optimizing the refrigerant charging amount, Efficiency can be improved.

  As mentioned above, although embodiment of the heat source machine which is one of the heat exchange units which concerns on this invention was divided into 8 embodiment, it was combined with any of Embodiment 1-8. May be configured. Moreover, although only one embodiment of the load side machine that is one of the heat exchange units according to the present invention has been described, the same configuration as the heat source machine that combines any of the first to eighth embodiments Can be applied. Furthermore, only one embodiment of the air conditioner according to the present invention has been described. However, the heat source apparatus according to any one of the first to eighth embodiments and the first to eighth embodiments are combined. The load side machine which combined either can be combined arbitrarily. For example, the air conditioner 100 can be configured with the heat source unit 1a-2 according to the second embodiment and the load side unit having the same configuration as the heat source unit 1a-6 according to the sixth embodiment.

  DESCRIPTION OF SYMBOLS 1 Compressor, 1a-1 to 1a-8 Heat source machine, 2 Control box, 2a Load side machine, 3 Centrifugal fan, 3a 1st centrifugal fan, 3b 2nd centrifugal fan, 4 Heat exchanger, 4-1 1st heat Exchanger, 4-2 Second heat exchanger, 4a heat exchanger, 4b heat exchanger, 5 housing, 6 bypass air passage, 7 air inlet, 8 drain pan, 9 bypass partition plate, 10 air outlet, 11 fan partition Plate, 13 Fan motor, 14A Intake air path, 14B Blow air path, 15 Heat transfer pipe, 16 Round pipe, 17 Flat pipe, 18 Fin, 19 Refrigerant distribution pipe, 20 Refrigerant collecting pipe, 21 Corrugated fin, 22, 22a, 22b Heat exchanger, 23 Heat exchanger, 24 Pressure reducing device, 25 Flow path switching device, 26 4th connection piping, 27 5th connection piping, 28 6th connection piping, 29 1st connection piping, 30 2nd connection piping, 31 3rd connection piping, 34 gas-liquid separator, 35 bypass piping, 37 flow control device, 40 bell mouth, 41 partition plate, 42 blowing air channel, 43 suction blowing partition plate, 45 fan inlet, 100 air conditioner, 100A Air conditioner.

Claims (8)

An intake air passage that communicates with the air inlet and a blowout air passage that communicates with the air outlet are formed, and among the height, width, and depth dimensions, the housing having the smallest height dimension;
A first partition plate that vertically divides the interior of the housing into the intake air passage and the blowout air passage;
A bell mouth installed at the periphery of the opening formed in the first partition plate;
A centrifugal fan which is adapted to be blown air circumferentially through said bell mouth installed on the first partition plate, the outlet air passage,
A heat exchanger disposed inside the housing and downstream of the centrifugal fan,
The casing has two main plates in the upper and lower directions that are the rotation axis direction of the centrifugal fan, and a front surface, a rear surface, a first side surface, and a second side surface as side surfaces in the rotation direction of the centrifugal fan,
The outlet is formed with an opening in the front,
The air intake opening is formed in the rear surface,
The intake air passage is formed so as to reach the rear surface between a fan intake port that is an intake port of the centrifugal fan and the main plate closest to the fan intake port.
The heat exchanger has upper and lower heat exchangers on the front side of the centrifugal fan,
The lower heat exchanger is inclined so that the outlet side is on the top and the centrifugal fan side is on the bottom,
The upper heat exchanger is disposed so as to be inclined such that the outlet side is on the lower side and the centrifugal fan side is on the upper side ,
The intake air passage is prevented from reaching the front surface of the housing by a suction blow-off partition plate that partitions the intake air passage and the blow-off air passage;
The heat exchanger is a heat exchange unit that is disposed closer to the air outlet than the suction / air outlet partition plate . The housing is rectangular in top view, and the front surface in which the air outlet is formed and the rear surface in which the air inlet is formed are surfaces along the long side direction of the rectangular shape in top view,
The centrifugal fan is arranged so that the first centrifugal fan and the second centrifugal fan are aligned in the long side direction,
Said heat exchanger, the heat exchange unit according to claim 1 which is installed so as to continue from the front side of the first centrifugal fan toward the front side of the second centrifugal fan. The centrifugal fan is arranged so that the first centrifugal fan and the second centrifugal fan are arranged in the casing.
The first centrifugal fan and the second centrifugal fan are positioned so that the center of the first centrifugal fan and the center of the second centrifugal fan are located on different straight lines parallel to the width direction of the casing. The heat exchange unit according to claim 1, further comprising a fan. The casing has a compressor for compressing a refrigerant flowing in the heat exchanger inside,
The compressor heat exchanger unit according to any one of claim 1 to 3 arranged close to the corners of the rear surface side of the housing than the centrifugal fan. A housing in which an intake air passage communicating with the air inlet and a blowout air passage communicating with the air outlet are formed;
A first partition that divides the interior of the housing into the intake air passage and the blowout air passage;
A bell mouth installed at the periphery of the opening formed in the first partition plate;
A centrifugal fan installed on the first partition plate via the bell mouth;
A heat exchanger disposed inside the housing and downstream of the centrifugal fan,
The inlet is
An opening is formed on any surface of the housing forming the intake air passage,
The air outlet is
An opening is formed on any side surface of the casing forming the blowing air path,
The intake air path is
It is formed so as to reach the rear surface between the fan inlet that is the inlet of the centrifugal fan and the main plate closest to the fan inlet,
The heat exchanger is disposed at a position facing at least two of the side surfaces of the housing so as to surround the centrifugal fan,
A second partition plate that forms a bypass air passage that guides air that has passed through the heat exchanger disposed at a position far from the air outlet in the heat exchanger to the air outlet is provided in the air outlet. Replacement unit. The heat exchange unit according to claim 5 , wherein a part of a fan motor that rotates the centrifugal fan is protruded from the bypass air passage. When the height of the housing is H1, and the height of the bypass air passage is H3,
The heat exchange unit according to claim 5 or 6 , wherein the bypass air passage and the housing are configured such that (H3 / H1) is in a range of 10% to 40%. A refrigerant circuit in which a compressor, a first heat exchanger, a decompression device, and a second heat exchanger are connected by piping;
The load side machine is equipped with the first heat exchanger,
The compressor and the second heat exchanger are provided in a heat source machine,
At least one of the heat source unit and the load side unit is the heat exchange unit according to any one of claims 5 to 7. An air conditioner.

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